CN101881272A - Variable vane pump - Google Patents
Variable vane pump Download PDFInfo
- Publication number
- CN101881272A CN101881272A CN201010175622XA CN201010175622A CN101881272A CN 101881272 A CN101881272 A CN 101881272A CN 201010175622X A CN201010175622X A CN 201010175622XA CN 201010175622 A CN201010175622 A CN 201010175622A CN 101881272 A CN101881272 A CN 101881272A
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- CN
- China
- Prior art keywords
- slider
- spring
- pump
- variable vane
- vane pump
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
- F04C2/3442—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
- F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
- F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
- F04C14/226—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam by pivoting the cam around an eccentric axis
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16N—LUBRICATING
- F16N13/00—Lubricating-pumps
- F16N13/20—Rotary pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/04—Force
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/16—Wear
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Rotary Pumps (AREA)
Abstract
A kind of variable vane pump (10) comprising: the entrance and exit in pump body (13); Be rotatably installed in the live axle (16) in the pump body (13); The rotor (14) that driven shaft (16) drives; Be arranged in a plurality of radially extended blades (15) in the described rotor (14) slidably.Slider (11) is arranged in the central axis that the axis that is eccentric in described rotor (16) was gone up and had to pivot (19) pivotally.A plurality of fluid chamber (17) limit and one after the other are connected to entrance and exit by described rotor (14), described blade (15) and described slider (11).Resilient member (12) cooperates pivotally with described slider (11) and acts on described slider (11) to be gone up to promote described slider (11) along a direction.
Description
Technical field
The present invention relates to a kind of variable vane pump (variable displacement vane pump), relate more specifically to a kind of variable vane pump of engine lubrication system of motor vehicle.
Background technique
The lubrication system of motor is assigned to the engine lubrication loop by pump (such as variable vane pump (VDVP)) to lubricating fluid (for example, oil) pressurization and with it.Variable sliding blade pump can use rotor and slider, and this slider has a plurality of slidably blade and cavitys of radially extending that can change the fluid volume that is sent to lubricating loop.Slider is from the biasing of rotor eccentricity ground, to form the fluid chamber that is limited by blade, rotor and slider internal surface.Pressure spring makes the slider location to form big fluid chamber acquiescently.
When motor needed the fluid of the smaller size smaller that pump provides or less oil pressure, pressure regulator guided to fluid the adjusting chamber of pump from the pump outlet line.The pressure of regulating in the chamber pivots slider antagonistic spring power, so that closely align in the center of rotor and slider, reduces the size of fluid chamber thus.This reduced from fluid reservoir etc. be inhaled into the amount of the fluid the pump, by the amount of the fluid of pump output, and also reduced oil pressure thus.
U.S. Pat 6,763,797 have disclosed a kind of variable displacement pump, and wherein, pump discharge pressure is used to make the location bias of slider (also becoming cam ring), changes the degree of eccentricity of slider with respect to rotor axis thus, and changes pump displacement thus.By changing pump displacement with respect to pump discharge pressure, pump discharge pressure can be based on the motor traffic demand and controlled.The pressure control characteristic of pump is determined the hydraulic coupling of this antagonistic spring negative function on slider by demarcating antagonistic spring.
But, also expect further improvement to variable vane pump, and the variable vane pump that particularly has the pivoted slider that is used for engine lubrication system.
Summary of the invention
The invention provides a kind of variable vane pump, wherein, cooperated pivotally with slider by the resilient member that promotes against slider with the slider that can pivot.
Pivoted cooperation between resilient member and the slider is used for reducing stress on the resilient member at slider when resilient member pivots, and reduces the bending of resilient member and the generation of warpage.Therefore, the serviceability of spring and variable vane pump can be increased.In addition, the result as its installation can be reduced because of the generation that wearing and tearing on the spring increase the warpage that causes.Because spring constant can be increased, fuel consumption also can reduce.
Variable vane pump can comprise following feature: the pump body, entrance and exit in described pump body, be rotatably installed in the live axle in the described pump body, by the rotor of described drive shaft be arranged in a plurality of radially extended blades in the described rotor slidably.Variable vane pump also can comprise the pivot (pivot) that is arranged in the described pump body, be arranged on the described pivot pivotally and have the axis that is eccentric in described rotor central axis slider and limit and one after the other be connected to a plurality of fluid chamber of entrance and exit by described rotor, described blade and described slider.Resilient member acts on the described slider, and promoting described slider along a direction, and the pressure control chamber is arranged between the outer surface of described pump body and described slider.As mentioned above, resilient member cooperates pivotally with slider.
In one embodiment, resilient member is bias voltage between pump body and slider, to promote slider along a direction.Resilient member can be biased slider is pushed to the end position of its range of pivot.In one embodiment, resilient member the pump body and from the outer surface of slider bias voltage between the outstanding protuberance.
In one embodiment, when resilient member pivoted, resilient member pivoted around the pivot at pump body place at slider.
Resilient member can comprise the spring with longitudinal axis, such as the spring of spiral winding.
Spring also can comprise a portion, and it cooperates pivotly with slider.Seat portion also can cooperate slidably with slider.
In one embodiment, seat portion comprises concave outer surface, and this concave outer surface cooperates slidably with nonreentrant surface on being positioned at slider.The concave outer surface of seat portion and the nonreentrant surface of slider can have the form that is locked to each other and cooperates.
In one embodiment, seat portion also comprises the guide finge of extending from the flat internal surface relative with described recessed surface.Guide finge is contained in the described spring.Guide finge can have longitudinal axis, if resilient member comprises helical spring, this longitudinal axis is roughly parallel to or extends along helical spring longitudinal axis.The flat internal surface of seat portion can be approximately perpendicular to the longitudinal axis of spring and the longitudinal axis of guide finge.Guide finge can have the length shorter than the length of pressure spring not, so that allow spring to be compressed by slider under installation conditions.
In one embodiment, spring is against the flat internal surface bias voltage of seat portion, and promotes seat portion against slider.If seat portion has outer recessed surface, this outer recessed surface can be pushed against the nonreentrant surface that is positioned on the slider by spring, and this spring is against the flat internal surface bias voltage of seat portion.
In one embodiment, when seat portion pivoted, the longitudinal axis of spring pivoted around the point at pump body place at slider.
In another embodiment, along with the longitudinal axis of spring pivots against the point that seat portion pivots on the pump body because of slider, the outer surface of seat portion cooperates slidably with slider.Compare with the layout that between spring and slider, does not slidably cooperate, between spring seat portion and the slider this is slidingly matched feasible, the flat internal surface of seat portion is orientated with the longitudinal axis of more vertical mode with respect to spring, and with the end face orientation of more parallel mode with respect to spring.The increase that this has further reduced the stress on the spring and can cause the serviceability of spring and pump.
The present invention also provides a kind of lubrication system of motor car engine, and it comprises a described variable vane pump among the embodiment as described above.Lubricant medium by this pump pumping can be an oil.
But, being not limited in the lubrication system of motor car engine, use according to one variable vane pump in the previous embodiment, its leaf can be used for the liquid or the gas of other type of pumping, for example pumped air in other is used.
Description of drawings
With reference to accompanying drawing embodiment is described.
Fig. 1 shows the viewgraph of cross-section according to variable vane pump of the present invention;
Fig. 2 shows the 3-D view of a part of the variable vane pump of Fig. 1;
Fig. 3 shows the detailed view of pivoted spring of the variable vane pump of Fig. 1;
Fig. 4 shows the viewgraph of cross-section of reduced parameters's vane pump;
Fig. 5 shows pivoted spring and the slider of Fig. 1;
Fig. 6 shows the angular displacement of pivoted spring and the slider of Fig. 5;
Fig. 7 shows the detailed view of the pivoted spring of Fig. 6;
Fig. 8 shows the schematic representation of the pivoted spring of Fig. 7.
Reference character
10 variable vane pumps
11 sliders
12 springs
13 pump case
14 rotors
15 blades slidably
16 fixed axis
17 pumping chambers
18 shell body walls
19 pivots
20 longitudinal axis
21 guide finge
22 portions
23 concave outer surfaces
24 flat internal surfaces
The end face of 25 springs
The nonreentrant surface of 26 protuberances
27 pivots
28 end positions
The pivotal action of 29 sliders
30 protuberances
The slidably cooperation of 31 portions and protuberance
The skew of 32 springs
The skew of the spring in the 33 contrast pumps 10 '
10 ' reduced parameters's vane pump
The slider of 11 ' contrast pump 10 '
The spring of 12 ' contrast pump 10 '
The pump case of 13 ' contrast pump 10 '
The rotor of 14 ' contrast pump 10 '
The slidably blade of 15 ' contrast pump 10 '
The fixed axis of 16 ' contrast pump 10 '
The pumping chamber of 17 ' contrast pump 10 '
The shell body wall of 18 ' contrast pump 10 '
The pivot of 19 ' contrast pump 10 '
The longitudinal axis of 20 ' contrast pump 10 '
Embodiment
Fig. 1 shows the viewgraph of cross-section according to variable vane pump 10 of the present invention.Variable vane pump 10 comprises the slider 11 that can pivot, and this slider is promoted along a direction by resilient member, and this resilient member has the form of helical spring 12.The 3-D view of spring 12 and slider 11 is shown in Figure 2, and spring 12 can be shown in Figure 3 with respect to the motion of slider 11.
When pump 10 stopped, slider 11 was pushed to maximum eccentric position with respect to rotor 14 by spring 12.When pump was operated with slider 11 in this position, pump delivery was in its maximum value.Along with slider 11 pivots (representing with arrow 29 in the accompanying drawings) from the maximum centrifugal position, pump delivery reduces, and the output flow of pump reduces substantially usually.When the center of slider 11 is pivoted to a position of aliging with the axis 16 of rotor 14 in this center, slider 11 is in 0% the degree of eccentricity (that is, maximum eccentricity is 100%), and pump 10 is operated with 0 discharge capacity.
Unshowned oil-in is formed on the inlet side of housing 13, and unshowned compressed oil outlet is formed on the opposite outlet side of housing 13.Entrance and exit is communicated with pumping chamber 17 so that prevent gas entrapment in pumping chamber 17, and this pumping chamber is preferably on the relative bottom and top side of rotor 14.The rotation that is in the rotor 14 of an eccentric level causes 17 expansions of pumping chamber.The variation of chamber volume causes the step-down of pumping chamber thus, and this causes oil to be drawn into pumping chamber 17 by inlet, and releases pumping chamber 17 along with the chamber contraction and by outlet then.
Except spring 12, resilient member comprises the guide finge 21 of the seat portion 22 with one.Guide finge 21 has the length littler than the length of the spring that is mounted, and guide finge is concentrically positioned in the spring 12, thereby extends along the longitudinal axis 20 along spring 12 roughly.Seat portion 22 have outer recessed surperficial 23 with this outer recessed surperficial 23 relative flat internal surface 24.Flat internal surface 24 is approximately perpendicular to the length of guide finge 21 and longitudinal axis 20 ground of spring 12 extend.The end face 25 of spring 12 is roughly parallel to the planar surface 24 of a portion 22.
Outer recessed surperficial 23 of seat portion 22 cooperates slidably with nonreentrant surface 26, and this nonreentrant surface is positioned at from the surface of the outstanding protuberance 30 of the outer surface of the slider 11 that can pivot.This is slidingly matched and shows in Fig. 3 by arrow 31.
Fig. 4 shows the viewgraph of cross-section of the reduced parameters's vane pump 10 ' with the slider 11 ' that can pivot.In this reduced parameters's vane pump 10 ', resilient member only comprises spring 12 ', and this spring extends between the planar surface 26 ' of the protuberance 30 ' of slider 11 '.Planar surface 26 ' is approximately perpendicular to the longitudinal axis 20 ' of spring 12 ' and is parallel to the end face 25 ' of spring 12 '.
Fig. 5 shows the operation of the pivoted spring 12 and the slider 11 that can pivot of variable displacement pump shown in Figure 1.Three positions of spring 12 and slider 11 are shown in Fig. 5 and 6.Spring 12 and slider are around their respective pivot 27; 19 angular displacement is being used for shown in Fig. 6 of each position, 7 and 8.
But an end points of the range of pivot of slider 11 illustrates by reference character 28 in the accompanying drawings.When slider 11 was in the end position 28, guide finge 21 and spring 12 were provided so that their longitudinal axis 20 is approximately perpendicular to pump case 13.The position that end position 28 can be had maximum volume usually by the fluid chamber 17 of slider 11 limits.
Along with slider 11 pivots in the plane of slider 11 counterclockwise around pivotal point 19, spring 12 is compressed and the nonreentrant surface 26 of protuberance 30 cooperates slidably with recessed surperficial 23 of seat portion 22, causes guide finge 21 and spring 12 to pivot clockwise around the pivotal point 27 at pump case 13 places thus.Along with the angular displacement increase of slider 11, that is, slider 11 pivots in the counterclockwise direction, and guide finge 21, seat portion 22 and spring 12 further pivot along clockwise direction.
Because the pivotal action of guide finge 21 is compared with slidably arranging under the situation about being omitted of seat portion 22 and protuberance 30, planar surface 24 maintenances of seat portion 22 are more parallel and more perpendicular to the longitudinal axis 20 of spring 12 with respect to the end face 25 of spring 12.The end face 25 of spring 12 and its change against the angle between the surface of bias voltage reduce make the stress on the spring 12 reduce, thereby the possibility of spring 12 warpages reduces.The serviceability of spring 12 and pump and life-span can improve.
Fig. 6 to 8 shows two angular displacements of the slider 11 of the pump 10 among the Fig. 1 that is provided with the spring 12 that can pivot away from end position 28.When slider 11 pivots 4 ° the time counterclockwise from end position 28, make the longitudinal axis 20 of guide finge 21 and spring 12 pivot 3 ° along clockwise direction.The planar surface 24 of seat portion 22 is caught to pivot 2.5 ° clockwise.
When slider 11 pivots 8 ° the time counterclockwise from end position 28, make the longitudinal axis 20 of guide finge 21 and spring 12 pivot 6.7 ° along clockwise direction.The planar surface 24 of seat portion 22 is caught to pivot 6.2 ° clockwise.
The contrast of offset path that has the spring 12 ' of the spring 12 of a portion 22 and contrast pump 10 ' in the slider side has been shown among Fig. 8.The offset path that has the spring 12 of a portion 22 in the slider side illustrates by solid line 32, and the skew in the spring 12 ' in the contrast pump 10 ' of Fig. 4 is illustrated by dotted line 33.
The skew of pivoted spring 12 with pivoted spring 12 of guide finge and seat portion 22 is linear.On the contrary, the spring 12 ' of pump 10 ' has the non-linear skew in band maximum displacement zone.In addition, the displacement of the spring 12 ' of contrast pump 10 ' is greater than the displacement of the spring of arranging according to the present invention 12.
For pump 10 ' shown in Figure 4,4 ° of angular displacements of slider 11 ' cause 7 ° of the longitudinal axis displacements of spring, and cause the planar surface of a portion to pivot 4.5 ° clockwise.
For 8 ° slider angular displacement, if the end face of spring 12 ' cooperates with the non-slidably planar surface of protuberance 30 ', 14.7 ° of the longitudinal axis displacements of spring, and the planar surface of seat portion pivots 8.5 ° clockwise.Compare the bigger stress of spring 12 ' experience, and so easier generation warpage of spring with arrangement according to the invention.
Claims (13)
1. a variable vane pump (10) comprising:
Pump body (13);
Entrance and exit in described pump body (13);
Be installed in the live axle (16) in the described pump body (13) rotatably;
By the rotor (14) of described live axle (16) driving;
Be slidably arranged on a plurality of radially extended blades (15) in the described rotor (14);
Be arranged in the pivot (19) in the described pump body (13);
Be arranged in the slider (11) on the described pivot (19) pivotally, this slider has the central axis of the axis that is eccentric in described rotor (16);
Limit and one after the other be connected to a plurality of fluid chamber (17) of entrance and exit by described rotor (14), described blade (15) and described slider (11);
Resilient member (12) acts on the described slider (11), to promote described slider (11) along a direction;
Wherein, resilient member (12) cooperates pivotally with described slider (11).
2. variable vane pump as claimed in claim 1 (10), wherein, resilient member (12) is bias voltage between pump body (13) and slider (11).
3. variable vane pump as claimed in claim 2 (10), wherein, resilient member (12) pump body (13) and from the outer surface of slider (11) bias voltage between the outstanding protuberance (30).
4. as the described variable vane pump (10) among the claim 1-3, wherein, when resilient member (12) pivoted, the pivot (27) that resilient member (12) is located around pump body (13) pivoted at slider (11).
5. as the described variable vane pump (10) among the claim 1-4, wherein, resilient member (12) comprises the have longitudinal axis helical spring (12) of (20).
6. variable vane pump as claimed in claim 5 (10), wherein, spring (12) also comprises a portion (22), this one cooperates pivotally with slider (11).
7. variable vane pump as claimed in claim 6 (10), wherein, seat portion (22) cooperates slidably with slider (11).
8. as claim 6 or 7 described variable vane pumps (10), wherein, seat portion (22) comprises concave outer surface (23), and this concave outer surface cooperates slidably with nonreentrant surface (26) on being positioned at slider (11).
9. as the described variable vane pump (10) among the claim 6-8, wherein, seat portion (22) also comprises the guide finge (21) of extending from the flat internal surface (24) relative with described recessed surface (23) of this one (22), and described guide finge (21) is contained in the described spring (12).
10. variable vane pump as claimed in claim 9 (10), wherein, the flat internal surface (24) of seat portion (22) is approximately perpendicular to the longitudinal axis (20) of spring (12).
11. as claim 9 or 10 described variable vane pumps (10), wherein, spring (12) is against flat internal surface (24) bias voltage.
12. as the described variable vane pump (10) among the claim 5-11, wherein, when seat portion (22) pivoted, the pivot (27) of the longitudinal axis (20) of spring (12) on pump body (13) pivoted at slider (11).
13. the lubrication system of a motor car engine comprises as the described variable vane pump (10) among the claim 1-12.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB0907687.8A GB2470012B (en) | 2009-05-05 | 2009-05-05 | Variable Displacement Vane Pump |
| GB0907687.8 | 2009-05-05 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101881272A true CN101881272A (en) | 2010-11-10 |
| CN101881272B CN101881272B (en) | 2014-12-24 |
Family
ID=40792243
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201010175622.XA Expired - Fee Related CN101881272B (en) | 2009-05-05 | 2010-05-05 | Variable displacement vane pump |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US8602749B2 (en) |
| CN (1) | CN101881272B (en) |
| DE (1) | DE102010015288A1 (en) |
| GB (1) | GB2470012B (en) |
| RU (1) | RU2010117636A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102364205A (en) * | 2011-10-24 | 2012-02-29 | 上海幸福摩托车有限公司 | Variable displacement oil pump |
| CN102537631A (en) * | 2011-12-22 | 2012-07-04 | 湖南机油泵股份有限公司 | Three-way type variable slide block control structure of oil pump with variable discharge capacity |
| CN102980016A (en) * | 2012-12-03 | 2013-03-20 | 湖南机油泵股份有限公司 | Three-level variable displacement vane oil pump |
| CN103062612A (en) * | 2012-12-28 | 2013-04-24 | 宁波圣龙汽车动力系统股份有限公司 | Oil pump with variable displacement |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US9206800B2 (en) | 2012-05-18 | 2015-12-08 | Magna Powertrain Inc. | Multiple stage passive variable displacement vane pump |
| DE102012220832A1 (en) | 2012-11-15 | 2014-05-15 | Robert Bosch Gmbh | Vane pump for conveying fluid e.g. lubrication oil into lubrication system for motor car, has two hydraulic units which respectively move working chamber housing relative to rotor or rotor relative to housing in respective directions |
| ITTO20130392A1 (en) * | 2013-05-16 | 2014-11-17 | Vhit Spa | ADJUSTABLE DISPLACEMENT ROTARY PUMP WITH OPTIMIZATION OF ADJUSTMENT MEANS OF CONTRAST, AND METHOD FOR ADJUSTING THE PUMP DISPLACEMENT |
| JP6177610B2 (en) * | 2013-07-17 | 2017-08-09 | 日立オートモティブシステムズ株式会社 | Variable displacement pump |
| JP6165019B2 (en) | 2013-10-21 | 2017-07-19 | 日立オートモティブシステムズ株式会社 | Vane pump |
| CN103742775A (en) * | 2013-12-30 | 2014-04-23 | 东风汽车公司 | Vane variable displacement oil pump |
| JP6540421B2 (en) * | 2015-09-24 | 2019-07-10 | アイシン精機株式会社 | Variable oil pump |
| CN113915509A (en) * | 2021-09-30 | 2022-01-11 | 宋宇希 | Variable-displacement rotor oil pump |
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| US5752815A (en) * | 1995-09-12 | 1998-05-19 | Mercedes Benz Ag | Controllable vane pump |
| CN101042133A (en) * | 2006-03-23 | 2007-09-26 | 株式会社日立制作所 | Variable displacement vane pump |
| CN101240724A (en) * | 2007-02-06 | 2008-08-13 | 通用汽车环球科技运作公司 | Pressure regulating variable displacement vane pump |
| US20080308062A1 (en) * | 2007-06-14 | 2008-12-18 | Hitachi, Ltd. | Variable Displacement Pump |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| ATE340569T1 (en) | 2002-02-18 | 2006-10-15 | Ajinomoto Kk | USE OF A NEW AGENT TO PREVENT INFECTIONS |
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- 2010-04-17 DE DE102010015288A patent/DE102010015288A1/en not_active Withdrawn
- 2010-05-04 US US12/773,631 patent/US8602749B2/en not_active Expired - Fee Related
- 2010-05-04 RU RU2010117636/06A patent/RU2010117636A/en not_active Application Discontinuation
- 2010-05-05 CN CN201010175622.XA patent/CN101881272B/en not_active Expired - Fee Related
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| US5752815A (en) * | 1995-09-12 | 1998-05-19 | Mercedes Benz Ag | Controllable vane pump |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102364205A (en) * | 2011-10-24 | 2012-02-29 | 上海幸福摩托车有限公司 | Variable displacement oil pump |
| CN102537631A (en) * | 2011-12-22 | 2012-07-04 | 湖南机油泵股份有限公司 | Three-way type variable slide block control structure of oil pump with variable discharge capacity |
| CN102980016A (en) * | 2012-12-03 | 2013-03-20 | 湖南机油泵股份有限公司 | Three-level variable displacement vane oil pump |
| CN103062612A (en) * | 2012-12-28 | 2013-04-24 | 宁波圣龙汽车动力系统股份有限公司 | Oil pump with variable displacement |
| CN103062612B (en) * | 2012-12-28 | 2015-09-09 | 宁波圣龙汽车动力系统股份有限公司 | Displacement-variable oil pump |
Also Published As
| Publication number | Publication date |
|---|---|
| US8602749B2 (en) | 2013-12-10 |
| DE102010015288A1 (en) | 2010-11-11 |
| RU2010117636A (en) | 2011-11-10 |
| US20100282204A1 (en) | 2010-11-11 |
| GB0907687D0 (en) | 2009-06-10 |
| GB2470012B (en) | 2016-04-27 |
| GB2470012A (en) | 2010-11-10 |
| CN101881272B (en) | 2014-12-24 |
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